One-way clutch



Aug. 2, 1960 F. E. ULLERY 2,947,395

ONE-WAY CLUTCH Original Filed April 18. 1952 ONE-'WAY CLUTCH Fred E. Ullery, 8-2'3'1 Marygrove Drive, Detroit, Mirc h.,

@riginal application Apr. 18, 1952-, Ser. No. 283,090-, now Patent No. 2,762,198, dated Sept. 11,-,` 1956. Di@- vided and this application .luneV 22 1,956, Ser. No. 593,131 e 2 Claims. (Cl. 19k-45.2)-

This is a divisional application, the par-entY application being Serial No. 283,090, tiled April 18 1952, and' titled Member Spacing Construction invIe-Iydrodynamic Torque Converters; and from which Patentl No. 2,762,198 issued September ll, 1956.

This divisional application is tiled consonant with a requirement to restrict `the claims ofjtlhe designatedl ,I )arent` application; andV relates to subject matter which was fully disclosed, in` the parent applicatiom being thus qnalitied for the benefit of the filing date thereof, i

The inventionset forth in this application relates to a one-way clutch for rendering-` two coaxial components of a machine one-Way rotatory, one to. the other. disclosed herein for three different pairs of components in ahydrodynamic torque converter, the basic construction ofA this one-way clutch has important fundamental advantages, one unusual advantage being expedient adaptability for specific physical circumstances and functional` needs. The construction basically includes: a `drum having a smooth cylindrical outer surface; a support ring having a smooth cylindrical inner surfacetdisp/osed; around the druni outer surface to. bound an annular space therebetween; a plurality of sprags arranged around the annular space to eect one-way jamming operative to render the drum and the support ring one-way rotatory, one to the other;l and, e. plurality oi compression type springs. ofi coil form,v each spring being disposed with its coil axis oblique from the circumferential trend' off the annular space ond interposed between two adjacent sprags to urge the outer end of one and the inner end of the other in opposite circumferential directions to induce prompt jamming. action- The ism-urging arrangement, which is believed to bc novel, is essential for and, leads to ciective attainment of some of the objectively sought advantages..`

One important object of the invention is to achieve high capacity for transmitting torque through,` the oneway clutch in the jammed and clutched direction tol thus minimize the space required for its accomnn.;datioittv and to accordingly improve its utility. FIfhe agreeable physical correlation of the jamming sprags and the jam-urging means furthers circumferential compactness so that a large number of the sprsss may be accommodated around, the stated annular space. The torquetransrnitting capacity for given proportions being approximately proportional to Vthe number of jamming elements, high capacity is accoidingly obtained-` A Another important object is to further eliiciency of the device and durability of its features for the free-whirling operation during which relative rotation exists between the opposing elements, that is, between the drinn and the support ring- This operation. involves sliding, action, between notional-gripping surfaces; and; etilectve attain.- rncnt of this objective requires minimization of the dii: fgelclltial velocity and the frictional drag of that` Vsliding action, and also, avoidance of sculiing damage by abrupt and ycyclic transitions of the sprags als` a group from rotational unisonance with the drum to thatwith the sup- States arent O port ring, and vice versa.

ICC

2 The characteristics of thepresent jam-inging means are unusually favorable for and contribute to these attainments.

In commonly known spragftype one-way clutches, in which the jam-urging means is a spiral-Wound spring of garier form having a tensile band influence on the sprags, the radial `component of the, jam-urging means is inward and opposite tothe centrifugal forces which vary with the rotational speed ofgthe sprags as a group; so, the sprags rotate with Athe drum or 'with the support ring, withV fre,` quent abrupt transitions from one to the other, according yto the respective predominance of these inward and out: Wardl radial forces.`

Contrariwise, the present jam-urging means exerts a compressive circumferential force, the resultant radial influence on the sprags being outward like the centrifugal forces and actingl therewith torcause rotation of the sprags with the support tina. thereby avoiding the aforestatefl transitions and4 tcuilingto restrict the stated sliding action to. the reletiucly low dilicrential velocity between the, inner ends of. the shrugs and the cylindrical Surface of the drum.

Also. regarding, centrifugclinlluence on the intensity of the. ioni-urging notion, the present iam-urging Ineens permits! the spree crosse-sectional forni. to. be that which resucctively` expedient for the specic operation of the particular, one-wey. clutch. For the embodiment which is, roost. fully disclosed herein, both the drum andthe. sun-A uort riua rotate, and one-Way clutching must be avail: ble. over-a widelspecd reuse; accordingly, the anlrur s action should. be frcs from centrifugal influences furtherance oi which, the spree` crossrscctiousl 'forni su h that the spree. center. of gravity is, maintained cn.- oro mately in radial cligumentvvith the spr-eg outer contact with; the support, rin-a However, for `criollos-r illustrated. embodiment, the support ring free-whine for- Wordly relative to the drum, and clutching occurs, only when` the drum is stationary and the support ring, tends, to rotate backwardly; hence, centrifugal counteraction of the. icrhrursing action is advantageous, in furtherance oi which, theA sorua cross-sectional forinrustyv bc that. hav-` ing the sprayss center of gravi-ty appropriately Qffsci. fIQI-ll radial alignment with the sprag outer end contact with the support, ring l` Another obiectis to. improve reliability and responsiveness, ot the jans-urging action. This involves minfnnizeftion of inertie, frictiohal and viscous. returning factor-s; the last-named beine especially important for cold -wenther operation of a one-way clutch, submerged oil,V Ei: fective accomplishment of this objective is evidenced: by the almost negligible weight of the springs which serve as the. jam-urging means; bythe fact'that-the springs acl;- directly onthe sprass, Without sliding action; und by freedorh of the rhysicel forni of the issu-urging;- uesns from significant entrapment of fluid and viscous drag.

Still another, object is. to `further ense and economy of manufacture. Only rtsinhll number-ot types of causare required inasmuch asl the present invention does not ref. (1u-,ire supplementary structure. either for circumferential spa-eins of the sprsssor for locating curl retaining the icm-urging Ineens` Esch of the parte, the the suce port ring,` the sipna-es,` and the, springs, of the basic con:l struction has asimple physical forni and lends itselfto, economical manufacture by known production uitethofls..v

These objects and advantages, and others., will be. nr-V pcccnt to persons skilled in. the art troni, the-ensuing dev scription in connection with the accompanying4 d rawingg, in which: e i' A e Fig. 1 is a longitudinalfragmentary section of a hydrodynamic torque converter showing the central pofrt'ofn thereof,1 as cut` by a radial plane containing the axisofijotation, and illustrating advantageous usage of` one-way- 3 clutches 370, S07 and 593, each of which is an embodiment of the present invention;

Fig. 2 is an enlarged section of one-way clutch 370, inclusive of elements or fragments of elements which are structurally associated with that clutch for the particular usage, the plane of this section being the same as that of Fig. l;

Fig. 3 is a section of`one-way clutch 370, inclusive of elements structurally associated therewith, taken on, and axially viewed as directionally indicated at, line 3 3 of Fig. 2, but having one spring and fragments of the drum, the support ring and two sprags deleted so as to distinctly show the termini of lines leading from reference characters to specific features; and,

Fig. 4 is a View of two adjacent sprags 380 which are Vsomewhat enlarged and are oblquely exploded apart so as to show the neighboring sides and the opposing springseats thereof.

In describing the operation of each of the illustrated embodiments, respective forward and backward rotational tendencies and characteristics are pointed out for the torque converter components with which the drum and the support ring of the particular one-way clutch are rotationally united, respectively; the direction of forward rotation being as indicated by a directional arrow FR in each of Figs. l, 2 and 3. v Fig. 1 shows, for a hydrodynamic torque converter, a central construction including: a central portion of each of live bladed members, namely, turbine 3Ta, stator 3Sb, stator 38a', turbine 3Tb, and pump SPa; a fragmentary portion of a casing end cover 311, which is usually adapted for rotational association with a power source so as to transmit power therefrom to the torque converter; a turbine hub 340 which, serving as an intermediary component of a driven structural train, has turbine 3Ta firmly attached thereto and is rotationally united with the torque converter output power shaft 342; and, a hollow reaction shaft 518 which has a stator hub 560 rotationally united with its front (innermost) end, and has its back end formed integral with the drum element of one-way clutch 507 which is shown in a functionally suitable relationship witha fragmentary portion of a stationary support structure 517. Also, as shown, stator 3Sa is rotationally united with the stator hub S60 which also includes a portion which is the drum element of one-Way clutch 593 through which stator 3Sb is associated with that stator hub.

Regarding functional rotational influences effected between components ofthe torque converter by the exemplified embodiments of the present invention: one-way clutch 370 permits forward rotation but prevents backward rotation of end cover 311 relative to the rotationally united turbine hub 340 and output power shaft 342; one-way clutch 507 permits forward rotation and prevents backward rotation of the rotationally united stator 33a', stator hub 560 and reaction shaft 518 relative to the stationary support structure 517; and, one-way clutch 593 permits forward rotation and prevents backward rotation of stator 3Sb relative to the stator hub 560.

For normal transmission of power, the rotational tendencies of stators 3Sb' and 3Sa are naturally such that stator 3Sa' never tends to rotate forwardly unless stator 3Sb is .so rotating; and when both are rotating forwardly, the speed of stator `3Sb is faster than that of stator 3Sa. So, the disclosed construction is suitably operative for rendering each of stators 3Sb' and 38a rrn against backward rotation and rotative forwardly; thus being operative for each of these stators to render a respective array of blades backwardly rm for their utilitarian purposes, but forwardly yielding to avoid directional influences which would be detrimental.

Regarding one-way clutch 370, some of the functional advantages and physical requirements ofthe particular adaptation may be comprehended from its usage in the drive train of an automobile, for which, it renders the 4 'r1 coast-drive mechanically positive through the torque converter; thereby, affording more engine-braking effort for downhill operation, reducing the speed required for pushstarting of the engine, and avoiding engine stumbling and dying while the automobile has any forward motion whatsoever.

In the enlarged sectional View of Fig. 2, for which the plane of the section is the same as for Fig. 1; the elements of one-way clutch 370 and those of a bearing are more distinctly shown structurally arranged and correlated together and with components of the torque converter in a compact combination construction which, not only permits forward rotation and prevents backward rotation of the end cover 311 relative to turbine hub 344), but radially centers and axially locates turbine hub 340 with respect to end cover 311. The illustrated bearing is a balltype which includes an outer race 332, an inner race 334, and an intermediary circular-row of balls 331; but, it is contemplated that other types of bearings may be used with appropriate physical adaptations. V

The support ring 321 of one-way clutch 370 and the outer race 332 of the stated lbearing are associated with end cover 311, the association of the bearing outer race being through the support ring, as forthwith described. The support ring 321 is centered with, and is abutted against an inside (back side) surface of, the end cover 311. The outer race 332 is centered and axially lixed with the support ring 321, being situated in the circular mounting 333 thereof, and being interposed and axially confined between the front side surface of the race retainer disc 326 and the back side surface of the sprag guide disc 329 which is shouldered in the support ring. A plurality of circumferentially spaced screws 322 axially fix and rotationally unite the race retainer disc 326 with the support ring 321, and that support ring with the end cover 311, each screw passing through those elements, and having an encircling seal 324 and an external fastening nut 323.

The drum 371 of one-way clutch 370 and the inner race 334 of the stated bearing are associated with the turbine hub 340. Specifically described, the inner race 334 is centered on a circular mounting 335 of the turbine hub 340, and is axially fixed therewith, being interposed and axially confined between the turbine hub front side surface 343 and the annular back side surface 371 of the drum 371 which is rotationally united and axially retained with the turbine hub, respectively, by mating splines 373, and by the snap ring 345 which is situated in the turbine hub ring groove 344 and abuts the front side of the drum 371.

For the ensuing description of elements and physical features which effect the jam-urging action and the oneway jamming and clutching operation of one-way clutch 370, attention is directed to Fig. 3 which is a sectional Viewy taken on line 3-3 of Fig. 2, and to Fig. 4 which is a View of two adjacent sprags 380 somewhat enlarged and ob-V liquely exploded apart. The support ring 321 has a smooth cylindrical inner surface 378 which is concentrically disposed around, and radially spaced apart from, a smooth cylindrical outer surface 372 of the drum 371. These surfaces bound an annular space occupied by a plurality of one-way jamming sprags 380, spaced somewhat adjacently around that annular space.

Each of the sprags has: at its outer end, a smooth gripping surface 379 in axial line contact with the support ring inner surface 378; and, at its inner end, a smooth 'gripping surface 381 in axial line Contact with the drum outer surface 372. Y The distance between the inner and the outer axial lines of contact of each sprag is slightly greater than the radial distance between the drum outer surface 372 and the support ring inner'surface 373; so that, the lines of contact of each sprag lie in a respective plane which is slightly oblique from the particular radial plane that contains the respective inner line of contact, each sprag being oblique in the same angular direc-v e tion. The permissible angle of obliquity depends some.- what on the influence of the jam-urgingY means; otherwise, for the sprag smooth surface jamming and frictionalgripping, the tangent of the angle of Obliquity at an axial line of contact must not exceed the coefficient of friction existing at the particular contact.

In the preceding paragraph, the contacts of the sprag gripping surfaces with the drum and the supportV ring surfaces were referred to as axial lines of contact in order to clearly describe the relative disposition of the sprags. Actually, these contacts exist as lines only for light contact pressures. The pressures are very high at these contacts when much torque is transmitted in the jammed direction, and the surfaces are consequently compressed into axial bands of surface Contact, of which, the lines of effective pressure represent the nominal linesl of contact.

For the free-whirling operation, the pressure at the outer line of contact of a sprag exceeds that at its innerline of contact due to the circumferential expanding tendency of the circular array of sprags, that expanding tendency being exerted by the compression type springs 376 of the jam-urging means, the features of which are presently described. Also, for an embodiment such as oneway clutch 370, in which the array of sprags rotate, centrifugal effects further add tothe pressure existing at the outer line of contact of each sprag. So, except for occasional and progressive creep, the circular array of sprags rotationally remains with the support ring.

Hence, for an abutting relationship of adjacent sprags for assuring proper circumferential spacing, it is preferable that such a relationship should be near the outer ends of the sprags 380; whereat, asshown in Fig. 3, a toe 386 of each sprag abuts, or nearly abuts, a heel 387 of an adjacent sprag. Also, near the inner ends of the sprags 380, there may be a similar abutting relationship of the toe 384 and the heel 385 of adjacent, sprags, but usually with somewhat more clearance.

Regarding the jam-urging means,r it is preferable that a separate spring 376 be included between each two adjacent sprags, as shownV in Fig. 3. Therein, a jam urging spring 376 of compression type and of coil form is compressed and interposed between each pair of opposing sides of adjacent sprags 380, as follows: one end coil is situated in a spring seat 383 in the side of, and near the outer end of, one of the two adjacent sprags; and the opposite end coil is situated in an opposing spring seat 382` in the opposing side of, and near the inner end of, the other one of the two adjacent sprags. Thus, each spring 376 is disposed with its coil axis considerably oblique from tangency with an imaginary circle (of which any arc 3Cr is illustrated) which is concentric with the drum outer surface 372, and intersects the spring coil axis midway between the coil ends. As shown, the springs 376 urge the inner and the outer endsV of the sprags 380 in the opposite circumferential directions conducive to jamming.

For an embodiment having a separate spring between each two adjacent sprags, such as shown in Fig. 3, the respective jam-urging action on each sprag may be separately comprehended, as follows: each sprag 380 has an opposing pair of spring seats 382 and 383 which are olset` from each other so that the respectivethrusts of the springs 376, at the opposite sides of each sprag, induce a moment acting on and urging eachV sprag towards radial disposition into the jamming situation with the drum 371 and the support ring 321.

In the foregoing description, it is stated that it is considered preferable that a jam-urging spring be included between each. two adjacent sprags; however, it is realized that some of the jam-urging springs 376 shown in Fig. 3 may be omittedif, for the sprags between which the springs are omitted, the abutting relationships of the toes 384 and 386 respectively with the heels 385 and 387 agregar 6 are. made, suciently, accurate, tot elfect; simultaneous jamming and releasing ofthe particular sprags.

Also, it isrealized that with appropriate modifications, an embodiment of this one-way clutch between twoV com..- ponents of a machine may serve as the radial bearing means' for supporting one component relative to the other. With suitable clearance limitations: of the sprag toe to heel relationships to properly restrict the released disposition of the sprags 380, and thus to' limit the radial clearance between the sprag surfaces 381 and. thedrum surface 372, the multiplicity of these sprag surfaces` simu,- late, for sliding action relative to the drum surface,` a ramp type of radial bearing which is adequate to radially support a` light Weight component,` such as, either the stator 3Sb or the back end of the reaction shaft 518 of Fig. l.

In some embodiments requiring considerable radial bearing capacity, several groups of sprags may be replaced by slipper type bearing blocks. For example, in a one-way clutch in which eighteen sprags suthce. to ful,- ll the torque transmitting needs, and in which` there is circumferential spacel to accommodate :about thirty sprags, eighteen sprags in three groups of six sprags and three intervening bearing blocks may be used. Each of the three bearing blocks should have an o'uter arcuate surface which is contiguous and conforms with the support ring surface 378, and an inner arcuate surface in radial bearingl association, with the drum surface 372. The opposite ends of each bearing block should have features comparable to those of aV sprag as regards the spring seats 382 and 383, the toe 386 and the heel 38.7; but the toe 384 and the heel 3815, which are near the drum surface, should beA somewhat abbreviated to avoid interference with the adjacentsprags as regards `the slight rocking motion essential to proper jamming :and releasing actions.

I'n the forepart of this specification, some of the objects and advantages of this one-way clutch invention are set forth with4 brief explanations. Effective realizations of these objectively sought advantages are; manifested in the ensuing comments,I wherein contributory and essen.- tial factors and influences are pointed out with adequate explanations; the factors and influences being physical features and characteristics disclosed in the illustrations and. the foregoing descriptions and explanations. Also, the ensuing commentsV point out fulllments of special needs for various operating conditions which are exemplifed by the three embodiments illustrated in Fig.4 1

That this one-way clutch has` usually large capacity f or transmitting torque in the jammed and clutched direction is quite evident from a consideration of fundamental principles applied to the disclosed features. At each fric,- ti'onal-gripping contact ofa jamming element, the peripheral force component is small relative to the radial force component which tends to crush the surfaces; the, transfV mittable magnitude of the peripheral force being accordingly limited. Thus, for given physical proportions and material properties, the` torque transmitting capacity of a one-Way jammingv and frictional-gripping clutch is approximately proportional to the number ofjamming elements.

As shown in Fig. 3, the novel arrangement of the jam urging springs 376 with the sprags 380 is quite compact, and an unusually large number of sprags is accordingly accommodated. Thus, for a specific torque transmitting requirement, the physical size of the one-way clutch may be unusually small. This is an important advantage for an application where the torque transmitting requirement is large and space is in demand, such as, the applications of one-way clutches 370 and 507 shown in Fig. l.

Regarding efficiency of this one-way clutch invention and the durability of its features for the free-whirling operation, which involves sliding action of frictiorialgripping surfaces, the invention has physical features and eharacteristcs which are especially appropriate and advantageous for the free-whirling operation.

Along'with the aforesaid objects and advantages, it is pointed out -that in some of the wellaknown sprag-type one-way clutches, there are conflicting influences affecting the rotation of the sprags and the sliding action: the nature of the jam-urging means tends to cause the sprags to rotate with the drum, whereas, the centrifugal effects of rotation tends to cause the sprags to rotate with the support ring; consequently, there may be abrupt and cyclic transitions of the sprag rotational status from one to the other.

For the present invention, as pointed out and explained in the description of the features disclosed in Fig. 3, the predominant radial force exerted on the sprags by the jam-urging means is directionally outward, the same as the centrifugal effects;V consequently, the array of sprags always tends to rotationally remain with the support ring, Thus, detrimental transitions are prevented, and the sliding action tends to be restricted to the relatively low diier'ential velocity between the sprag inner end surfaces 381 and the 4drum surface 372.

Another advantage, which furthers enieiency and durability for the free-whirling operation, is that the physical form of the jam-urging means permits the sprag crosssectional form to be that which, for the particular operating conditions, is most expedient as regards the intensity of the jam-urging action. Appropriate utilization of this advantage is explained forthwith for each of two of the disclosed embodiments, namely, one-way clutches 370 and 593 of Fig. l.

ln one-way clutch 37th, which prevents forward speed lag of the end cover 311 relative to the turbine hub 34d, one-way jamming and clutching is required over a wide speed range; for instance, in a vehicle drive application, the sprags must jam and grip whenever the vehicle coastsl irrespective of the actual speed of the vehicle. Of course, undue intensity of the jam-urging action in any portion of the Vspeed range would cause undesirable frictional drag for the free-whirling operation. To provide proper ,iam-urging action over the speed range without excessive intensity of the action in any portion, the jarrburging action should be nearly free from centrifugal influences; in furtherance of which, the sprag crosssectional form should be such that each of sprags 380 has its center of gravity approximately in radial alignment with the axial line of contact of its outer surface 379 at the support ring surface 373. For the slight variation in sprag Obliquity from the jammed to the released disposition, this radial alignment tends to be maintained by the roiling action at the surface contact and the attendant circumferential shift thereat of the axial line of contact.

In one-way clutch 593, which permits forward rotation but prevents backward rotation of stator SSb relative to stator hub 560', the conditions are such that stator hub 56d is always stationary when stator 3Sb tends to rotate backwardly. Hence, when jamming. is needed, there are no centrifugal influences. For the free-whirling operation in this application, centrifugal moderation of the intensity of the jam-urging action is desirable. To effect this moderation, the sprag cross-sectional form should be such that each of the sprags has its center of gravity offset from radial alignment with its outer end Contact at the support ring, so that, the centrifugal outward force induces a moment which is counteractive of the jarr1-urging actiom- Thus, for the free-whirling operation frictional drag of the sliding action is reduced.

.o te only elements of the jam-urging means being the very light weight springs 376; absence offrictional drag or hysteresis is shown by the fact that the springs 3:76 act directly on the sprags 38u without sliding action; and.

viscous impediment is minimized as indicated by the unusual freedom of the jam-urging means from fluid entrapment and viscous drag influences. Q t

l Regarding ease and economy of manufacture, an important advantage of this one-way clutch invention is that a supplementary structure is not required either for circumferential spacing of the sprags or for locating and retaining the jam-urging means. Thus, only a small number of types of parts are required; and, as regards essential features, each of these parts may be economically manufactured by known production methods. Specifically, the formations of the cylindrical surfaces, namely, the outer surface of the drum andthe inner surface of the support ring, are common inexpensive operations; the jam-urging springs may be produced from coiled wire stock on an automatic spring forming machine; and the sprags may be processed as sections cut off of stock rolled and proled in strip form, which is a process used for producing sprags of well-known one-way clutches.

Although a Vpreferred embodiment of this one-way clutch invention has been described in detail, it is, of course, understood that the invention is not limited to the particular forms and structuressliown in the drawings, or otherwise revealed, for disclosure and explanatory purposes, but also embraces modifications within the scope of the appended claims.

l claim:

l. A oneway clutch adaptable for rendering two' coaxial components of a machine one-way rotatory, one to the other, and comprising: a drum having a smooth cylindrical outer surface; a support ring having a smooth cylindrical inner surface disposed around said drum outer surface to bound an annular space therebetween; a plurality of one-way`jamming sprags arranged around said annular space, each of said sprags being disposed with an axial line contact with said drum outer surface and an axial line contact with said support ring inner surface and with the plane of said contacts 1oblique from radial disposition to effect one-way jamming operative to render said drum and said support ring onesway rotatory one to the other, and each of said sprags having a pair of spring seats which, one to the other, are situated on circumferentially-opposite sprag sides and are radially offset; and jam-urging means for said sprags including a plurality of compression type springs of coil form having end coils situated in said spring seats and disposed soV that a spring thrust is transmitted to each seat of each said pair of spring seats, each of said springs being disposed with its coil axis oblique from tangency with Aan imaginary circle which intersects its coil axis midway between its opposite end coils and is concentric with said drum outer surface, and each of said spring seats being disposed for normal squareness with the coil axis of the particular spring which is situated thereat, said urging means thus being operative to induce said one-Way jamming action simultaneously for each of said sprags.

2. The combination defined in claim l in which each sprag of said plurality of sprags has respective toe and heel features which are arranged in toe to heel relationship between circumferentially successive sprags to therefore form circumferential-spacing and action-synchronizing means.

References Cited in the file of this patent (-7 UNlTED STATES PATENTS 2,268,376 Dodge Dec. 30, 194i .i FOREIGN PATENTS 1,047,637 France July 22, 1953 

